Lateral connector for tube assembly

ABSTRACT

A coupling element having two ends, and outer surface and a longitudinal axis extending between the ends, wherein the first end of the coupling element defines a sealing surface where extends normally to the longitudinal axis and the outer surface of the other end defines a cam follower surface forming an angle on the range of from about 2 to about 10 degrees with respect to the longitudinal axis and wherein the second end defines the cam follower surface and the coupling element defines a passage extending from the sealing surface to the outer surface and apparatus comprising the coupling element and valve elements.

This application is a divisional of Ser. No. 08/361,357 filed Dec. 21,1994 now U.S. Pat. No. 5,582,438, issued Dec. 10, 1996.

BACKGROUND OF THE INVENTION

This invention relates to sealing lateral connections in tubular goods.In one aspect, the invention relates to sealing lateral connections inoilfield tubular goods.

Oilfield wells and wellheads have a characteristic architecture orarrangement. Wells and wellheads have a central vertical axis ofrotational symmetry. Installation & manipulation are by vertical axisdisplacement and/or vertical axis rotation. Cylindrical body members aretypical. Concentric nesting of cylindrical body members is also typical.Installation sequence of body members progresses from larger diameter tosmaller diameter. In the last analysis, a schematic representation of awellhead arrangement would suggest stacked cups.

The present invention addresses a need arising from this characteristicarrangement. Other devices or systems may share the same characteristicarrangement and might share in the benefit of the present invention.

The upper end of the wellhead system is closed by any one of a number ofdevices, providing control of fluid flow and pressure entering and/orleaving the well. This closure device is typically installed vertically,as a cap attached to the end of one of the wellhead's concentric bodycylinders, and sealing fluid pressure at the upper end of one or more ofthe body cylinders.

A basic function of a wellhead system is to provide for fluid flow intothe well and/or out of the well. The outer end of the requiredpathway(s) is outside of the outermost well barrier. The inner end ofthe pathway(s) is either the wellbore or one of the annular spacesbetween the concentric tubes or tubular bodies.

The basic flow in the pathway(s) is that of produced (or injected)fluids. This may include flow of well fluids which enter (or areintroduced into) the annular spaces in the system.

A second, but critical flow is that of pressurized fluids used tocontrol or operate devices in the well, such as downhole valves.

A less obvious need is the communication of non-fluid flow. Here afluid-tight pathway is used to allow passage of a cable, for electricalor even optical signals. Here a fluid-tight path is required to excludefluid rather than to contain it.

Examples of wellhead pathway connections are many. These include aconcentric vertical stab using a conventional single completion tubingbonnet (wing outlet above master valve); an eccentric vertical stabusing a dual, orienting tubing hanger and bonnet; a storm choke or SCSSVcontrol stab; a control system such as the Knerr et al control stabring, the Seehausen control connector, or NL control connections. Alsoincluded are these: concentric control line galleries on a side valvetree tubing hanger; an eccentric side penetrator (such as the BlizzardBOP tree control connector); or the Vetco shearable stinger.

Vertical connection of pathways is the most basic, typical approach. Itsmain advantage is that it relates well to the sequential "stack-up" ofthe system components. Also, it agrees with the installation motion,vertical displacement. Its disadvantages include these: that it requiresrotational orientation around the well axis if the path is notconcentric; it adds vertical stack-up height, and componentsubassemblies, to accommodate connection(s) and seals; it limits thenumber and size of connections into an annulus by its boundarydiameters.

Horizontal (radial) connection of pathways requires no rotationalorientation to the well axis if gallery seals are used. However, if ahorizontal connection (penetrator) crosses over a diameter interfacebetween two concentric bodies of the wellhead assembly, it "locks" thosebodies together and vertical displacement or removal of the inner fromthe outer body is prevented. Traditional "stab" connections(male/female) embody this disadvantage when configured in the horizontalorientation.

At the top of a completed wellhead system there is a tubing hangerinstalled in a tubing spool (or tubing bowl). Above this a bonnetprovides a transition and interface to the bottom connection of aChristmas tree.

In an arrangement of tubing hanger and tubing spool, regardless of whichconfiguration, there are basic boundary penetration requirements. Allmay be viewed as candidates for adaptation to horizontalpenetration/connection. The boundary penetrations are these:

1. pressurized control fluid; this operates downhole valves, or otherdevices;

2. annulus fluid (casing tubing annulus); this may be at pressure ornot, flowing or not, and may be "inbound" or "outbound";

3. production fluid; again, this may be at pressure or not, flowing ornot, and may be "inbound" or "outbound";

4. electric current; this may be low voltage and current, transmitting asignal to/from a downhole sensor or device. Alternatively this may be ahigh voltage and current transmitting power to a downhole device(usually a pump).

In typical tubing hanger arrangements penetrations for pressurizedfluid, including control fluid, have used a variety of designs. Thereare vertical, eccentric stabs (bonnet to hanger), as well as vertical,concentric connections (gallery seals, bonnet to hanger). Verticalconnections may require orientation, and utilize space inefficiently.Gallery seals, when used, add problems of leak paths and interflow.

Recently, horizontal fluid connections with push/pull stab connectionshave been proposed. In these systems the hanger, including its sidefacing female receptacles, is rotationally oriented to the spool. Thespool carries side facing male stabs, moved in/out radially byindependent actuators (generally, hydraulic with/without spring bias).The system requires orientation of the hanger in the spool.

Furthermore, as noted above, the horizontal stab system has as apotential failure mode the locking of the hanger in the spool if thestab fails to retract. In the commercial system it has been proposed todeal with this failure mode by providing a weak point in the stab,corresponding to the point at which it bridges the cylindrical interfacediameter between the hanger and the spool. In this way, failure toretract the stab can be overcome by forcibly withdrawing the hanger fromthe spool. In this action the stab will be sheared at its weak point.This allows for emergency recovery of the hanger, but leaves open thequestion of repairing the stab.

Typical electrical connections/penetrations have used verticalmale/female stabs, requiring orientation and alignment. Reliability ofthese items is a concern, and access to either half of the connection islimited, limiting effective maintenance and repair.

SUMMARY OF THE INVENTION

In one embodiment of the invention, there is provided a tubular assemblyhaving a lateral connection. The assembly comprises a tubular member, acarrier ring, a coupling element, and an urging means. The tubularmember has a generally cylindrical inside surface, an outside surface,and a longitudinal axis. The carrier ring has a generally cylindricalinside surface, a generally cylindrical outside surface, and alongitudinal axis. The carrier ring is positioned coaxially in thetubular member with the outside surface of the carrier ring positionedadjacent to the inside surface of the tubular member. The couplingelement is carried by the carrier ring. The coupling element has alongitudinal axis which is generally radially positioned with respect tothe longitudinal axis of the carrier ring. The coupling element has aninner end and an outer end. The outer end has a sealing face. A meansdefining a sealing face is provided on the inside surface of the tubularmember. The sealing face of the coupling element sealing engages thesealing face defined by the means on the inside surface of the tubularmember. A means is provided for urging the sealing face of the couplingelement and the sealing face defined by the means on the tubular membertogether responsive to relative longitudinal movement between the meansfor urging and the tubular member.

In another embodiment of the invention, there is provided a modular unitwhich can be used to establish a lateral connection through the sidewallof a tubular member positioned around it. The modular unit comprises acarrier ring, a coupling element, a carrier body, and a radial movementmeans. The carrier ring has a generally cylindrical inside surface and agenerally cylindrical outside surface. A coupling element is carried bythe carrier ring. The coupling element has a longitudinal axis which isgenerally radially positioned with respect to the longitudinal axis ofthe carrier ring. The coupling element has an inner end and an outer endand the outer end has a sealing face. A carrier body having a generallycylindrical outside surface is positioned coaxially inside of thecarrier ring. The generally cylindrical outside surface of the carrierbody is adjacent to the generally cylindrical inside surface of thecarrier ring. A means is provided for radially moving the couplingelement in the carrier ring responsive to relative longitudinal movementbetween the carrier ring and the carrier body.

According to another embodiment of the invention, there is provided amethod for establishing a line connection across a first tubular membersidewall. A carrier ring is provided which is concentrically positionedin the first tubular member. An annulus is defined between the carrierring and the first tubular member. A line coupling element is carried bythe carrier ring. The line coupling element has a longitudinal axiswhich is generally radially directed with respect to a longitudinal axisof the carrier ring. The line coupling element having an outer end whichdefines a first sealing face. A means is provided for defining agenerally radially extending passage through the sidewall of the firsttubular member with a second sealing face being defined at an inner endof the passage. The second sealing face is for sealingly contacting arespective first sealing face of the coupling element. A means isprovided for urging the sealing face of the first coupling element andthe sealing face at the inner end of the passage together in response torelative longitudinal movement between the first tubular member and themeans for urging.

In other aspects of the invention, there is provided a new couplingelement for connecting lines, a new carrier ring for carrying thecoupling element, a new carrier body for carrying the carrier ring, anew sliding actuator cam for actuating the coupling element, a newdetent for actuating the sliding actuator cam, and a new retractor forretracting the coupling element, as well as new cooperation between thevarious structural elements.

Horizontal, non-concentric penetrations offers several advantages to thedesigner.

1. reduced interflow risk

2. multiple radial connections on the same horizontal plane, savingstack-up height

3. simplified bonnet/tree cap

4. readier vertical access to the inner body (tubing hanger)

5. reduced risk of damage to seal surfaces in the spool, verticalscratching incurred in installation/removal of the inner body.

It is also apparent that the use of prior art horizontal, non-concentricpenetrator offers at least these two disadvantages:

1. failure to retract a stab may result in the need to shear out thestab body

2. a push/pull mechanism is built into the tree spool; this addscomplexity and failure modes to the item you wish to leave undisturbed.

The present invention provides a horizontal penetration which addressesthese two disadvantages "head-on".

First, this invention is designed to effect a face/face shear sealacross the cylindrical interface.

Use of a shear seal arrangement offers a number of advantages. Mostimportant and obvious is the advantage that the connection is separatedby lateral, shearing motion. In this application, that is the "motion ofchoice" in the installation and removal of the hanger from the spool.

Second, the invention provides a limited radial push/pull actuation by anovel mechanism on the inner (tubing hanger) body. This places themechanism on the preferred assembly for recovery and maintenance.

In addition, the use of a radial actuation, even a small one offersother advantages:

1. The shear seal interface is beneficially planar while the interfacehere is cylindrical. Use of the small radial displacement allowsinstallation of the inner (hangar) body with an unobstructed cylindricalspace.

2. Potential for damage to seal surfaces on installation and removal isreduced.

3. Positive energizing of the face seal is achieved.

4. Use of a metal seal is facilitated, because of the actuation.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will now be described, by way of example, withreference to the accompanying drawings in which,

FIG. 1 is an exploded perspective view of the subject invention;

FIG. 2 is an exploded perspective view of a penetrator according to thepresent invention;

FIG. 3 is a longitudinal section through the penetrator of FIG. 2;

FIG. 4 is a rear elevation of the penetrator of FIGS. 2 and 3;

FIG. 5 is a perspective view of a pawl used in the subject invention;

FIG. 6 is a perspective view of a retractor cam used in the presentinvention;

FIG. 7 is a perspective view of a sliding actuator cam or wedge used inthe present invention;

FIG. 8 is a side elevation, partially in section, of the cam or wedgeshown in FIG. 7;

FIG. 9 is a perspective view, partially broken away, of the carrier bodyof the present invention;

FIG. 10 is a perspective view, partially broken away, of the carrierring of the present invention;

FIG. 11 is a perspective view, partially broken away, of the orientationsleeve used with the present invention;

FIG. 12 is a detailed perspective view of a penetrator of the presentinvention, part of the carrier ring being broken away;

FIG. 13 is a section through the penetrator portion of the presentinvention, shown in a perspective orientation;

FIG. 14 is a section similar to FIG. 13, but on a different scale;

FIGS. 15 to 18 are vertical sections through a penetrator of the presentinvention showing sequential steps in the lowering and wedging actions;

FIG. 19 is a vertical section through the assembly incorporating thepresent invention in a test stand;

FIG. 20 is a perspective view an alternative version of the elements ofthe invention shown in FIGS. 7 and 5;

FIG. 21 is a perspective view of an alternative version of the elementof the invention shown in FIG. 7;

FIG. 22 is a reverse plan view of the elements shown in FIG. 20 isassembled form; and

FIG. 23 is a vertical section through the assembly incorporating thepresent invention in a well.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Overview

With reference to FIGS. 1 and 14, a preferred embodiment of theinvention comprises a first coupling element 20, sometimes referred toas a penetrator, a second coupling element 25, sometimes referred to asthe outer coupling, a carrier ring 30, a sliding actuator cam 35,sometimes referred to as a wedge, a retractor cam 40, sometimes referredto as a retractor fork, a pawl 45, sometimes referred to as a detent, acarrier body 50, a spool body 55, and a poppet valve 60.

Penetrator

One of the characterizing features of the invention is that at least onemovable penetrator 20 is used. It may be carried on either the carrierring 30 or the spool body 55. The radial movement of the penetratorsprovides for ample radial clearance between the carrier ring and thespool body to prevent damage to the seal faces.

The penetrator may be cylindrical or otherwise. Use of a large lateralclearance and small vertical clearance between the penetrator and its"port" in the carrier body gives advantageous limits on self alignment.This favors use of a rectangular, or even oval cross-section for thepenetrator, by allowing a tight vertical fit to the carrier ring(top/bottom), and a loose(r) lateral fit (side/side). The cylindricalpenetrator provides an equal fit all around, but is preferred on thebasis of manufacturing simplicity.

The penetrator is capable of mating a face/face electrical connection aswell as a fluid tight connection.

With reference to FIGS. 2-4, the coupling element 20 has a first end202, a second end 204, and outer surface 206, and a longitudinal axis208 extending between the first end and the second end. The first end202 forms a sealing surface 203 which extends generally normally to thelongitudinal axis 208. The outer surface 206 forms a cam followersurface 210 forming an angle in the range of from about 80 degrees toabout 88 degrees with respect to the longitudinal axis. Preferably, thecam follower surface 210 is defined by a portion of the outer surface206 at or near the second end 204. The coupling element 20 defines apassage 209 extending from the sealing surface 203 to the outer surface206. Preferably, the passage 209 extends from the sealing surface 203 toa side surface of the coupling element. A tubing line 213 is connectedto the passage 209 where it opens onto the side surface. As shown inFIG. 1, the tubing line is coiled to permit movement during installationand use. The tubing has an upper end and a lower end. It is attached byits upper end to the coupling element 20 and by its lower end to abulkhead 751 attached to the lower end of orientation sleeve 750. SeeFIG. 1.

In a preferred embodiment of the invention, the outer surface 206further defines at least one second cam follower surface 212 generallyforming an angle in the range of about 10 degrees to about 45 degreeswith respect to the longitudinal axis. For ease of fabrication, it ispreferred that the outer surface 206 be generally cylindrically shapedwith a generally circumferentially extending groove 214 and the at leastone second cam follower surface 212 is formed by a wall of the groove.

In one embodiment of the invention, the coupling element 20 has a valveseat 215 positioned in the passage 209 adjacent to the sealing surface203. The valve seat 215 faces away from the sealing surface 203. Thecoupling element 20 further comprises a valve element 216 positioned ina generally longitudinally extending portion 218 of the passage 209adjacent to the sealing surface 203. The valve element 216 has a valveface 220 to sealingly contact the valve seat 215. A means 222 isprovided in the passage 209 for biasing the valve element 216 toward thevalve seat 215.

Preferably, the valve element 216 has a first end 226 and a second end228 and the valve face 220 is positioned between the first end and thesecond end. The second end 228 of the valve element protrudes from thefirst end 202 of the coupling element 20 when the valve face 220 of thevalve element 216 is in sealing contact with the valve seat 215. SeeFIG. 3.

A plurality of grooves 240, 242 and 244 are preferably defined on thesealing surface 203 concentrically spaced around an inlet end 211 of thepassage 209. At least one seal element, preferably a plurality of sealelements 245, 246 and 247 are positioned in the plurality ofconcentrically spaced grooves, one seal element per groove. It iscontemplated that metallic C rings will provide good results when usedas the seal elements, optionally in combination with O ring seals.

Outer Coupling

Active or passive radial displacement could be built into the outer sealmember (static in the preferred embodiment). This could be in place ofor in addition to the displacement of the penetrators.

The contact face on the outer cylinder may be formed on a removablebody. This allows for easier manufacture (of the flat face). It alsoallows use of a different material from that of the cylinder. It allowsuse of hardfacing processes. It allows access for remote servicing ofthe inner penetrator by removing the outer body.

With reference to FIG. 14, the coupling element 25 has a first end 252and a second end 254. The coupling element has a flange 256 positionednear the first end 252 and a generally cylindrical nose-piece 258protruding from a face of the flange. The coupling element 25 forms apassage 260 extending from the first end 252 to the second end 254. Aland 262 (see FIG. 15) is defined by the second end of the couplingelement. In a preferred embodiment, the passage 260 is partially closedat the second end 254 of the coupling 25. The passage is divided into aplurality of openings 264 at the second end of the coupling element. Theopenings are preferably positioned in a generally annular pattern withthe land 262 being centrally located. The coupling element can be boltedto the sidewall of the spool body 55 using a plurality of bolts 268 toform a flow passage across the sidewall of the spool body. Preferably, aseal 266 is provided between the coupling element and the wall of thespool body. A BX seal is expected to provide good results whenpositioned in the vertical plane between the coupling 25 and the spoolbody 55.

Carrier Ring

With reference to FIG. 10, the carrier ring 30 has a first end 302, asecond end 304, and a longitudinal axis 306. A generally cylindricalouter surface 308 is positioned about the longitudinal axis and agenerally cylindrical inner surface 310 is positioned concentricallywith the outer surface 308. The carrier ring 30 defines a plurality ofgenerally radially extending boreholes 312 leading from the outersurface 308 to the inner surface 310 and a plurality of slots 316extending longitudinally along the generally cylindrical inner surface310. The slots extend from the first end 302 to the second end 304 ofthe carrier ring 30 and connect with the boreholes 312, one slot perborehole. The plurality of generally longitudinally extending slots 316are preferably each defined by a pair of sidewall surfaces 317 and abottom wall surface 321. Each sidewall surface preferably furtherdefines a generally longitudinally extending groove 323.

The carrier ring 30 preferably further defines a plurality of generallylongitudinally extending boreholes 320 extending from the first end 302to the second end 304. The generally longitudinally extending boreholes320 are spaced circumferentially apart from the generally radiallyextending boreholes 312.

It is further preferred that the generally cylindrical outer surface 308of the carrier ring 30 further defines a generally frustroconicallyshaped shoulder 324 near the second end 304. The generallyfrustoconically shaped shoulder 324 tapers toward the second end 304 ofthe carrier ring 30. If desired, a wiper seal not shown, can bepositioned between the borehole 312 and the second end 304 to clean theface of the outer coupling when the unit is lowered into position.

Wedge

With reference to FIGS. 7 and 8, the sliding actuator cam 35 has a firstend 352, a second end 354, and a longitudinal axis 356 extending betweenthe first end and the second end. The cam 35 has a first side surface358 positioned generally parallel to the longitudinal axis 356 and agenerally planar cam surface 360 on an opposite side of the cam 35 fromthe first side surface. The generally planar cam surface 360 extends atan angle in the range of about 2 degrees to about 10 degrees withrespect to the longitudinal axis 356. The cam 35 tapers from the firstend 352 to the second end 354.

The sliding actuator cam 35 preferably further has a first edge surface362 and a second edge surface 364 positioned generally parallel to thelongitudinal axis 356 and generally normal to the first side surface358. The sliding actuator cam 35 preferably is also provided with ribs.A rib 366 extends generally longitudinally along the generally planarcam surface 360. This rib is preferably centrally located and, whenpresent, forms the camming surface. A rib 368 extends generallylongitudinally along the first generally planar edge surface 362. A rib370 extends generally longitudinally along the second generally planaredge surface The first side surface 358 preferably further defines astep down 372 positioned between the first end 352 and the second end354 of the cam 35. The step down 372 is from a generally planar portion376 of the first side surface 358 and faces the second end of the cam35. The cam 35 preferably also defines a step up which faces the firstend 352 of the cam 35 and forms a shoulder 374 positioned between thestep down 372 and the second end 354. A lateral or channel groove 380 isthus formed between the step down 372 and the shoulder 374. The shoulder374 has an inner end 382 and an outer end 384. The outer end of theshoulder is spaced between the plane of the generally planar portion 376of the first side surface and the plane of the generally planar camsurface 360. Preferably, the shoulder 374 is generally planar and formsan angle in the range of from about 80 degrees to about 88 degrees withrespect to the longitudinal axis 356 of the cam 35.

In a preferred embodiment, a shaft 386 extends generally longitudinallyfrom a first end surface 388 of the cam 35.

Alternate Wedge

An alternate and presently preferred embodiment of the wedge isdescribed with reference to FIGS. 20 and 21. The sliding actuator cam635 has a first end 652, a second end 654, and a longitudinal axis 656extending between the first end and the second end. The cam 635 has afirst side surface 658 positioned generally parallel to the longitudinalaxis 656 and a generally planar cam surface 660 on an opposite side ofthe cam 635 from the first side surface. The generally planar camsurface 660 extends at an angle in the range of about 2 degrees to about10 degrees with respect to the longitudinal axis 656. The cam 635 tapersfrom the first end 652 to the second end 654.

The sliding actuator cam 635 preferably further has a first edge surface662 and a second edge surface 664 positioned generally parallel to thelongitudinal axis 656 and generally normal to the first side surface658. The sliding actuator cam 635 preferably is also provided with ribs.A rib 666 extends generally longitudinally along the generally planarcam surface 660. A rib 668 extends generally longitudinally along thefirst generally planar edge surface 662. A rib 670 extends generallylongitudinally along the second generally planar edge surface 664. Theribs serve the same function as in the cam 35.

The first side surface 658 further has an upper generally planar portion672 and a lower generally planar portion 674 positioned between theupper planar portion 672 and the second end 652 of the sliding actuatorcam 635. A step down 676 is defined between the upper planar portion 672and the lower planar portion 674. The lower planar portion 674 isdefined by a bottom wall of a lateral trough 678 extending across thefirst side surface and the bottom wall of a longitudinal trough 680extending from the second end 654 of the sliding actuator cam 635. Thelongitudinal trough connects with the lateral trough. The step down 676defines a first sidewall of the lateral trough.

A first boss 682 protrudes from the lower planar portion 674. The firstboss 682 has a first sidewall 684 defining a second sidewall of thelateral trough 678 and a second sidewall 686 defining a first sidewallof the longitudinal trough 680. A second boss 688 protrudes from thelower planar portion 674 at a position laterally spaced apart from thefirst boss 682. The second boss has a first sidewall 690 defining athird sidewall of the lateral trough 678 and a second sidewall 692defining a second sidewall of the longitudinal trough 680. Preferably,the second sidewall of the lateral trough and the third sidewall of thelateral trough 678 converge toward the second end 654 of the slidingactuator cam 635 and the first sidewall of the longitudinal trough 680and the second sidewall of the longitudinal trough converge toward thefirst end 652 of the sliding actuator cam 635. The sidewalls of thelateral trough preferably converge at an angle in the range of fromabout 160 degrees to about 176 degrees. The sidewalls of thelongitudinal trough preferably converge at an angle in the range of fromabout 45 degrees to about 120 degrees.

Retractor

One of the features of the present invention is that cammming of thepenetrator may include both engaging and disengaging of the opposedfaces. Disengaging of the opposed faces may be provided by the retractorfork.

With reference to FIG. 6, the retractor cam 40 comprises a base plate402 defining a first generally planar mounting face 404 and a pair ofspaced apart parallel retractor arms 406 mounted to the first generallyplanar mounting face 404. The retractor arms 406 protrude generallynormally from the first generally planar mounting face 404. Eachretractor arm has an inner end 408 attached to the first generallyplanar mounting face 404 of the base plate 402 and an outer end 410. Aside edge of each arm 406 forms a camming surface 412. The cammingsurfaces 412 of the pair of parallel retractor arms 406 lie in a singleplane which forms an acute angle with the first generally planarmounting face 404 of the base plate 402.

In a preferred embodiment, the base plate 402 has a first end 414, asecond end 416, and a longitudinal axis 418 extending between the firstend and the second end. The base plate 402 is longitudinally elongatedand has an opposed second generally planar mounting face 420 positionedgenerally parallel to the first generally planar mounting face (See alsoFIG. 13). The pair of parallel retractor arms 406 protrude from thefirst generally planar face 404 of the base plate in a directiongenerally normal to the longitudinal axis 418 of the base plate. Each ofthe pair of parallel retractor arms 406 is generally plate shaped and ispositioned in a plane which is generally normal to the longitudinal axis418 of the base plate. Each of the retractor arms has a first side edgeand a second side edge with the second side edge forming the cammingsurface. The second side edge is positioned at an angle in the range ofabout 10 degrees to about 60 degrees with respect to the first generallyplanar mounting face 404. Each of the parallel retractor arms 406 tapersfrom the outer end 410 to the inner end 408. More preferably, the outerend 410 of each retractor arm 406 is generally planar and is positionedgenerally parallel to the first generally planar face 404 of the baseplate. The outer end 410 meets the camming surface 412 at a point.

Detent

With reference to FIG. 5, the pawl 45 is formed from a first elongatedmember 452 having a first end 454 and a second end 456 and a secondelongated member 458 having a first end 460 and a second end 462. Thesecond end 462 of the first elongated member 452 is attached to thesecond elongated member 458 so that the pawl 45 is generally T-shaped.The first elongated member 452 has a first generally planar face 464 anda second generally planar face 466 (see also FIG. 14) and a toothelement 468 protruding from the first generally planar face 464 at aposition adjacent to the first end 454 of the first elongated member452. The tooth element forms a tooth face 470 spaced apart from thefirst end 454 of the first elongated member 452. The tooth face 470faces the second end 456 of the first elongated member. The tooth face470 is preferably generally planar and forms an angle in the range of 80degrees to 88 degrees with the first generally planar face 464 of thefirst elongated member 452. Preferably, the tooth element 468 furtherhas a camming face 472 located adjacent to the first end 454 of thefirst elongated member 452. The camming face 472 is preferably generallyplanar and is positioned in a plane which is positioned at an angle inthe range of from about 20 degrees to about 60 degrees with a planecontaining the first face 464 of the first elongated member 452.

It is further preferred that the elongated member 452 has a firstthickness and the second elongated member 458 has a second thicknesswhich is greater than the first thickness. This relationship causes astep 474 to be formed where the second face 466 of the first elongatedmember 452 is attached to the second elongated member 458.

Alternate Detent

An alternate and presently preferred embodiment of the detent isdescribed with reference to FIG. 20. A pawl 700 is formed from a firstelongated member 702, a second elongated member 704 and a connectingmember 706. The first elongated member 702 has a first end 708, a secondend 710, and a longitudinal axis. The second elongated member 704 has afirst end 712, a second end 714, and a longitudinal axis. The connectingmember 706 connects the second end 710 of the first elongated memberwith the second end 714 of the second elongated member. The firstelongated member is parallel to the second elongated member. Each of thefirst elongated member and the second elongated member has a toothelement 716, 718 protruding laterally from the elongated member at aposition adjacent to the first end. Each of the tooth elements forms atooth face 720, 722 spaced apart from the first end and facing thesecond end of their respective elongated member 702 and 704. Each toothface forms an angle in the range of about 80 degrees about to 88 degreeswith respect to the longitudinal axis of the elongated member.

Preferably, each tooth element 716, 718 further has a camming face 724,726 located adjacent to the first end of the elongated member. Thecamming face is positioned in a plane which forms an angle in the rangeof from about 20 degrees to about 60 degrees with the longitudinal axisof the elongated member. The camming face 724 on the first elongatedmember 702 faces away from the second elongated member 704 and thecamming face 726 on the second elongated member 704 faces away from thefirst elongated member 702. The tooth element 716 on the first elongatedmember 702 points away from the second elongated member 704 and thetooth element 718 on the second elongated member 704 points away fromthe first elongated member 702.

Preferably, the first elongated member and the second elongated membereach has a first thickness as measured transverse to the longitudinalaxis and the connecting member has a second thickness which is greaterthan the first thickness. A step 730 is formed where the first elongatedmember 702 and the second elongated member 704 connect to the connectingmember 706.

Carrier Body

With reference to FIG. 9, the carrier body 50 has a first end 502 and asecond end 504. The carrier body 50 has a generally annular flange 506positioned at the first end 504 and a generally tubular nose-piece 510protruding from a face 512 of the generally annular flange 506. Thenose-piece 510 has a generally cylindrical exterior surface 514. Theexterior surface 514 defines a plurality of channels 516 extendinggenerally longitudinally away from the generally annular flange 506. Theflange preferably defines a borehole 518 in longitudinal alignment witheach of the channels 516. Preferably, each of the channels 516 isdefined by a pair of sidewall surfaces 520 and a bottom surface 522.Each borehole 518 which is in longitudinal alignment with its associatedchannel 516 is spaced apart from the bottom surface 522 of the channel516. It is further preferred that the generally cylindrical exteriorsurface 514 further define a plurality of generally circumferentialchannels 524 extending generally circumferentially along the generallycylindrical exterior surface 514 of the nose piece 510 and crossing thegenerally longitudinally extending channels 516. Preferably, each of thegenerally longitudinally extending channels 516 is crossed by a firstgenerally circumferentially extending channel 526 and a second generallycircumferentially extending channel 528. The second generallycircumferentially extending channel 528 crosses the generallylongitudinally extending channel 516 at a second end 530 of each thegenerally longitudinally extending channels 516. It is further preferredthat the circumferentially extending channels 524 do not extendcompletely around the tubular nose piece 510, so that each generallylongitudinally extending channel 516 is crossed by a separate pair of afirst generally circumferentially extending channel 526 and a secondgenerally circumferentially extending channel 528.

OUTER COUPLING-SPOOL BODY

Certain embodiments of the invention require a means for defining apassage through the sidewall of the spool body and a means for definingan annular sealing surface on the inner sidewall of the spool body. Useof an outer coupling to define the radial flow passage and the sealsurface is optional but preferred. It is also preferred to provide aprotective diameter restriction in the spool above the connector (or torecess the seal surface from the inner surface of the spool) to preventthe seal surface on the connector from becoming damaged duringoperations. See FIG. 15 for shoulder 590 and recessing the outercoupling.

With reference to FIG. 19, the spool body 55, sometimes called a tubingspool comprises tubular member 550 defined by a sidewall 551. Thetubular member 550 has an inside surface 552, an outside surface 554, anupper end 556, and a lower end 558. The coupling element 25 extendsgenerally radially through the sidewall of the spool body. The first end252 of the coupling element is positioned adjacent to the outsidesurface 554 of the tubular member 550. The second end 254 of thecoupling element is positioned adjacent to the inside surface 552 of thetubular member. Preferably, the second end is positioned no higher thanthe inside surface.

OUTER COUPLING-PENETRATOR

When the outer coupling is used to form a radial passage through thespool body and the seal surface on the inner sidewall, it is preferredthat the outer coupling have a diameter greater than the diameter of thepenetrator. This permits access to the penetrator for servicing, such asreplacement of the seals.

The purpose of the penetrator/outer coupling connection is to establisha line connection to form a flow path for fluid or electrical currentflow. The sealing surfaces of the connectors mate to isolate the flowpath from the environment outside of the coupling connection.

With reference to FIG. 13, the second end 202 of the first couplingelement 20 defines sealing surface 203. The sealing surface 203 ispreferably generally annular and flat. A means 251 for forming a sealsurface on the inner sidewall of the spool body is provided by thesecond end 254 of the second coupling element 25. The second end 254defines a sealing surface 255, which is preferably generally flat andannularly shaped and is positioned in contacting relationship with thesealing surface 203 of the first coupling element 20. A plurality ofconcentrically positioned seal elements 245, 246, 247 are positionedbetween the annularly shaped generally flat sealing surface 203 of thefirst coupling element 20 and the annularly shaped generally flatsealing surface 255 of the second coupling element 25. Preferably, theseal elements are positioned in the plurality of concentrically spacedgrooves as previously described with reference to FIG. 2. A means 60 isassociated with the first coupling element and the second couplingelement for urging the first coupling element into sealing contact withthe second coupling element. The means 60 can be comprised by thecarrier ring 30, the sliding actuator cam 35, the pawl 45, the carrierbody 50, and the spool body 55.

The first coupling element 20 is movable from a first position in whichthe sealing surface 203 is spaced apart from the sealing surface 255 toa second position in which the sealing surface 203 is sealingly engagedwith the sealing surface 255.

OUTER COUPLING-POPPET VALVE

With reference to FIGS. 14 and 18, the first coupling element 20 has afirst end 202 and a second end 204 and defines a passage 209 extendingaway from the second end. The first coupling element defines a valveseat 215 positioned in the passage 209 adjacent to the first end 202 andfacing away from the first end 202.

The second coupling element 25 has a first end 252 and a second end 254.The passage 260 extends away from the second end 254. A land 262 for avalve body is located at the second end 254.

The valve element 216 is positioned in the passage 209 near the firstend 202 of the first second coupling element 20. The valve element has afirst end 226 and a second end 228 and a valve face 220 positionedbetween the first end and the second end which faces the second end 228of the first coupling element 20. The second end 228 of the valve body216 contacts the valve body land 262 on the second coupling element 25to hold the valve face 220 off of the valve seat 215.

A means 217 is associated with the first coupling element 20 for biasingthe valve body 216 toward the valve body land 262 and the first couplingelement 20 away from the second coupling element 25. A coil springpositioned in the passage 209 forms a suitable means 217.

A means 225 is associated with the first coupling element 20 and thesecond coupling element 25 for urging the first coupling element 20 intocontact with the second coupling element 25.

In the illustrated embodiment, the means 225 is formed by the carrierring 30, the sliding actuator cam 35, the carrier body 50, and the spoolbody 55.

The poppet valve body is movable from a first position in which thevalve face contacts the valve seat to a second position in which thevalve face is spaced apart from the valve seat and the valve is in theopen position. The valve body is carried by the penetrator and movesfrom the first position to the second position as the penetrator movesfrom the second position to the first position, due to the contact ofthe contact of the second end of the valve body with the valve bodyland.

PENETRATOR-CARRIER RING

When the penetrator is in the carrier ring, engaged against the outercoupling, and the wedge is fully engaged, slight vertical movement ofthe hanger body or carrier sleeve has no effect on the penetrator suchas unlock on sealing.

With reference to FIG. 12, the carrier ring 30 has a first end 302, asecond end 304, and a longitudinal axis. A generally cylindrical outersurface 308 is positioned about the longitudinal axis. A generallycylindrical inner surface 310 is positioned concentrically with theouter surface 308. The carrier ring 30 defines a plurality of generallyradial boreholes 312 extending from the outer surface 308 to the innersurface 310. A plurality of coupling elements 20 are slidably positionedin the boreholes 312, one coupling element per borehole. Each couplingelement 20 has a first end 202, a second end 204, an outer side surface207, and a longitudinal axis extending between the first end and thesecond end. The first end 202 forms a sealing surface 203 which ispositioned adjacent to the generally cylindrical outer surface 308 ofthe carrier ring. The sealing surface extends generally normally to thelongitudinal axis of the coupling element 20.

The penetrators are carried by the carrier ring. The penetrators areradially movable with respect to the carrier ring from a first positionas shown in FIG. 15 in which the sealing surface 203 slightly recessedradially inwardly from the outer surface 308 of the carrier ring 30 to asecond position as shown in FIG. 18 in which the sealing surface 203protrudes radially outwardly from the outer surface 308 of the carrierring 30. The movement is due to the action of the wedge 35.

PENETRATOR-WEDGE

The wedge could act other than on the radial inward end of thepenetrator. For example, the penetrator could include an o/d flange,interacting with a wedge "horseshoe" engaged over the penetrator body,in a manner similar to the illustrated retractor. The wedge could alsobe actuated in other ways. It could be actuated by weight set cammingmotion (wedge/carrier ring lands in spool, penetrators are driven overit), or by a separate actuator ring driven by the tubing hangerinstallation tool, or by integral hydraulic pistons.

It is important that the penetrator be seated squarely on the face ofthe outer coupling element in the spool. Misalignment of the penetratorin the carrier ring's radial port may interfere with this. Eccentricityof the carrier ring to the hanger and spool may also interfere withthis.

Misalignment in the horizontal plane can be "righted" by providing theinterface between the wedge and penetrator as a line of contact insteadof a plane (the camming surface on the wedge may be milled to a verynarrow vertical band; this contact at the center of the planar back faceof the (penetrator as illustrated).

Looking at loads on the penetrator in the horizontal plane, thisprovides a single, central actuating load on the penetrator. It allowsfor an eccentric reaction where the penetrator contacts the spool sealsurface. A moment results from the offset of these forces, acting toturn the penetrator to a right orientation in the horizontal plane.

With reference to FIG. 17, the coupling element 20 has an outer surface206, a first end 202, a second end 204, and a longitudinal axisextending between the first end and the second end. A portion of theouter surface 206 of the coupling element defines a cam follower surface210 forming an angle in the range of about 80 degrees to about 88degrees with respect to the longitudinal axis of the coupling element20. The sliding actuator cam 35 has a first end 352, a second end 354,and a longitudinal axis extending between the first end and the secondend. The sliding actuator cam has a generally planar cam surface 360lying in a plane which extends at an angle in the range of about 2degrees to about 10 degrees with respect to the longitudinal axis of theactuator cam. The cam surface 360 of the actuator cam 35 is positionedparallel to the camming surface 210 of the coupling element 20.Preferably, the cam surface 360 is formed by a rib 366. The longitudinalaxis of the coupling element 20 is positioned at a right angle withrespect to the longitudinal axis of the actuator cam 35. A means 65 isprovided for moving the actuator cam along its longitudinal axis to urgethe cam surface 360 of the sliding actuator cam 35 against the cammingsurface 210 of the coupling element 20 and cause the coupling element 20to move along its longitudinal axis. In the illustrated embodiment, themeans 65 comprises the carrier ring 30, the pawl 45, the carrier body50, and the spool body 55.

Preferably, the coupling element moves away from the longitudinal axisof the sliding actuator cam.

The wedge 35 is movable along its longitudinal axis from a firstposition as shown in FIG. 15 in which the cam surface 360 of the wedgeis spaced apart from the camming surface 210 of the coupling element 20to a second position as shown in FIG. 18 in which the cam surface 360 ofthe wedge 35 is in contact with the camming surface 210 of the couplingelement 20. As the wedge moves from the first position to the secondposition, the coupling element is moved from its first position to itssecond position. As the coupling element is moved, the cam surface movesalong the camming surface to wedge the coupling element radiallyoutwardly to make the seal.

PENETRATOR-RETRACTOR

With reference to FIG. 12, the coupling element 20 has an exteriorsurface 207, a first end 202, a second end 204, and a longitudinal axisextending between the first end and the second end. The exterior surface207 of the coupling element 20 defines at least one cam follower surface212. Each of said at least one cam follower surfaces 212 forms an anglein the range of about 10 degrees to about 60 degrees with respect to thelongitudinal axis of the coupling element 20. At least one retractor arm406 has a side edge forming a camming surface 412 positioned parallel tothe at least one camming surface 212 of the coupling element 20. A means70 is provided for moving the at least one retractor arm 406 at a rightangle with respect to the longitudinal axis of the coupling element 20to urge the cam surface 412 of the at least one retractor arm 406against the at least one camming surface 212 of the coupling element 20and cause the coupling element to move in a direction along itslongitudinal axis. In the illustrated embodiment, the means 70 comprisesthe carrier ring 30 and the carrier body 50.

The retractor arm is movable with respect to the penetrator from a firstposition as shown in FIG. 12 in which the cam surface 412 of theretractor arm contacts the camming surface 212 of the penetrator andlocates the penetrator in the first position to a second position asshown in FIG. 18 in which the cam surface 412 of the retractor arm isspaced apart from the camming surface of the penetrator and thepenetrator is in the second position. The movement of the retractor armis generally at a right angle with respect to the movement of thepenetrator.

PENETRATOR-POPPET VALVE

The spring loaded check valve in the penetrator is customary but,strictly, optional. Its presence allows pressure to be "locked" in theline to hold downhole valves open as tubing is being run. In addition,pressure thus locked in the line will vent as the valve is stabbed open.This will serve to clean the seal face as it is engaged. Notice finallythat it incidentally assists the retraction of the penetrator body intothe carrier ring.

With reference to FIG. 18, the coupling element 20 has a first end 202,a second end 204, and a longitudinal axis extending between the firstend and the second end. The coupling element 20 defines a passage 209having a first diameter extending from the first end 202 along thelongitudinal axis. The coupling element 20 has a valve seat 215 facingthe second end 204 positioned in the passage 209 adjacent to the firstend 202. A valve element 216 is positioned in the passage 209 adjacentto the first end 202. The valve element 216 has a valve face 220positioned to sealingly contact the valve seat 215 and a nipple 219having a second diameter which is smaller than the first diameterextending past the valve face 220 to protrude from the first end 202 ofthe coupling element 20 when the valve face 220 is positioned againstthe valve seat 215. A means 217 is associated with the valve element 216and the coupling element 20 for biasing the valve face 220 toward thevalve seat 215. In the illustrated embodiment, the means 217 is formedby a coil spring.

As previously discussed, the valve element is movable from a firstposition in which the valve face contacts the valve seat to a secondposition in which the valve element is spaced apart from the valve seat.

CARRIER RING-SPOOL BODY

If radial preloads on the penetrators are asymmetrical to the well axis,a net side load on the carrier ring will result. This must beaccommodated in some way, so that the carrier ring is not pushed offcenter. One technique is to provide a tight fit between the carrier ringand the spool, or alternatively, adequate clearances between ring,hanger and spool.

Use of cylindrical penetrators, as shown, offers some manufacturingbenefits, but is not ideal in theory. The design demands alignment ofthe penetrator to the seal face on the outer coupling element. Verticalalignment is assured by close dimensional tolerance in the relationshipof the stop shoulder and the penetrator. Lateral alignment is more of aproblem, depending on rotational orientation of the ring and spool,along with the magnitude of the interface diameter.

As a consequence, as previously noted, the ideal cross-section for thepenetrator is rectangular. This would allow a tight vertical fit to thecarrier ring (top\bottom). At the same time it would allow a loose(r)lateral fit (side/side). The cylindrical penetrator provides an equalfit all around, but is easier to manufacture.

With reference to FIG. 14, the spool body 55 is formed from a tubularmember 550 defined by a sidewall 551 having a generally cylindricalinner surface 552 and an outer surface 554 which is generally concentricwith the generally cylindrical inner surface 552. (See FIG. 19). Thetubular member 550 has a longitudinal axis. There is provided a means 75for defining a flow passage through the sidewall 551 of the tubularmember 550. The carrier ring 30 is defined by a sidewall 301 having agenerally cylindrical inner surface 310 and a generally cylindricalouter surface 308. (See FIG. 16). The carrier ring 30 has a longitudinalaxis and is positioned coaxially inside the tubular member 551 with thegenerally cylindrical outer surface 308 of the ring 30 being positionedclosely adjacent to the generally cylindrical inner surface 552 of thetubular member 55. A means 80 forms a flow passage through the sidewall301 of the ring 30. A means 85 is associated with the tubular member 550and the carrier ring 30 for aligning the means 80 for defining the flowpassage through the sidewall of the carrier ring 30 with the means 75for defining the flow passage through the sidewall of the tubular member550. In a preferred embodiment, the means 75 is formed by the couplingelement 25. The means 80 is formed by the coupling element 20. The means85 is formed by key 305 attached to the outer surface of the carrierring 30 adjacent the lower end thereof (see FIG. 12), which is receivedby a keyway 561 (see FIG. 13) in the tubular member 550.

A step in the diameter at the interface between the cylinder bodies,adjacent to the penetrator interface, can serve to help protect thefixed contact face from damage due to the passage of other elementsthrough the cylinder (such as tubing through the tubing spool).

Rotational alignment of the carrier ring 30 to the spool body isprovided as follows. An orientation sleeve 750 (see FIG. 1) is attachedto the lower end 504 of the carrier body 50 by radial bolts, not shown.The orientation sleeve 750 has an upper end 752 which is attached to thecarrier body and a lower end 754. (See FIG. 11) Slots 756 are providedat the upper end to permit passage of tubing leading from thepenetrators. A key 758 is attached to an outer generally cylindricalsurface of the orientation sleeve adjacent to the lower end 754. A helixsleeve 760 is attached to the inside surface of well tubing 762. Theupper end of the helix sleeve is formed into a tapering slot 764. Thelower end of the tapering slot 764 is sized to closely receive the key758. As the orientation sleeve 750 is lowered into the helix sleeve 764,the carrier ring 30 is rotated into alignment with the spool bodysufficient to permit key 305 attached to the outer surface of thecarrier ring 30 to be received by keyway 561 (see FIG. 13) in thetubular member 550 as the carrier ring bottoms against its stop.

CARRIER RING-WEDGE

With reference to FIG. 16, the carrier ring 30 has a first end 302, asecond end 304, a longitudinal axis, a generally cylindrical outersurface 308 positioned about the longitudinal axis, and a generallycylindrical inner surface 310 positioned concentrically with the outersurface. The carrier ring 30 defines at least one generally radiallyextending borehole leading from the outer surface 308 to the innersurface 310 and a generally longitudinally extending slot 316 along thegenerally cylindrical inner surface 310 from the first end to the secondend connecting with the borehole 312. The sliding actuator cam 35 has afirst end 352, a second end 354, a longitudinal axis extending betweenthe first end and the second end. The sliding actuator cam has a firstside surface 358 positioned generally parallel to the longitudinal axis,and a generally planar cam surface 360 on an opposite side of the cam 35from the first side surface. The cam surface 360 extends at an angle inthe range of about 2 degrees to about 10 degrees with respect to thelongitudinal axis. The sliding actuator cam 35 is slidably received inthe slot 316 of the carrier ring 30 for longitudinal movement. The firstside surface 358 faces the longitudinal axis of the carrier ring 30. Ameans 90 is associated with the carrier ring 30 and the sliding actuatorcam 35 for limiting radial movement of the actuator cam 35 in the radialdirection with respect to the longitudinal axis of the carrier ring 30.In a preferred embodiment, the means 90 comprises ribs 368, 370 (seeFIG. 7) which are received by grooves 323 (See FIG. 10).

The cam 35 is movable from a first position as shown in FIG. 15 to asecond position as shown in FIG. 18 with respect to the carrier ring 30.

CARRIER RING-CARRIER BODY

If radial preloads on the penetrators are asymmetrical to the well axis,a net side load on the carrier ring will result. This must beaccommodated in some way, so that the hanger is not pushed off center.One technique is to provide adequate radial clearances between ring,hanger and spool.

With reference to FIG. 15, the carrier body 50 has a first end 502, asecond end 504, and a longitudinal axis extending between the first endand the second end. The carrier body 50 is generally tubular and has agenerally annular flange 506 positioned at the first end 502 and agenerally tubular nose-piece 510 protruding from a face of the flange506. The nose-piece 510 has a generally cylindrical exterior surface514. The carrier ring 30 has a first end 302, a second end 304, andlongitudinal axis. A generally cylindrical outer surface 308 ispositioned about the longitudinal axis and a generally cylindrical innersurface 310 is positioned concentrically with the outer surface 308. Thecarrier ring 30 is coaxially positioned with respect to the tubularcarrier body 50 with the generally cylindrical inner surface 310 of thecarrier ring 30 being positioned closely adjacent to the generallycylindrical outer surface 514 of the tubular nose piece 510.

Spring bias can be provided between the inner cylinder and the carrierring to assure proper sequence of withdrawal or retraction of thepenetrator. A secondary detent can also be used to hold down the carrierring if the retraction forces are greater than the spring forces.

A mounting means 95 is associated with the carrier ring 30 and theflange 506 for slidably mounting the carrier ring 30 to the tubularcarrier body 50 in a fixed rotational orientation for movement from afirst position as shown in FIG. 15 to a second position, closer to theflange, as shown in FIG. 18. A biasing means 100 is associated with themounting means 95 for biasing the carrier ring 30 away from the flange506, toward the first position. As the carrier ring moves from the firstposition to the second position, the wedge moves from the firstposition, which is spaced apart from the penetrator, to the secondposition, in which it is in wedging relationship with the penetrator. Ina preferred embodiment, the means 95 is formed by bolts 96 to which thecarrier ring 30 is slidably mounted and which are threadably secured inthe flange 506. The biasing means 100 comprises coil springs 102surrounding the shafts of bolts 96 and positioned between the flange 506and the carrier ring 30 to urge the carrier ring away from the flange506. (See also FIG. 1).

WEDGE-CARRIER BODY

With reference to FIG. 15, the carrier body 50 has a first end 502, asecond end 504, and a longitudinal axis extending between the first endand the second end. The carrier body 50 is generally tubular and has agenerally annular flange 506 positioned at the first end 502 and agenerally tubular nose-piece 510 protruding from a face of the flange506. The nose-piece 510 has a generally cylindrical exterior surface514. The sliding actuator cam 35 has a first end 352, a second end 354,and a longitudinal axis extending between the first end and the secondend. The actuator cam 35 has a first side surface 358 positionedgenerally parallel to the longitudinal axis, and a generally planar camsurface 360 on an opposite side of the sliding actuator cam 35 from thefirst side surface 358. The cam surface 360 extends at an angle in therange of about 2 degrees to about 10 degrees with respect to thelongitudinal axis. The sliding actuator cam 35 is positioned withrespect to the tubular carrier body 50 so that the longitudinal axis ofthe sliding actuator cam 35 is positioned parallel to the longitudinalaxis of the tubular carrier body. The first side surface 358 of thesliding actuator cam 35 faces the generally cylindrical exterior surface514 of the generally tubular nose piece 510 and the sliding actuator cam35 tapers away from the generally annular flange 506.

Spring bias can be provided on the locking wedge to assure it stayslocked in the case of vibration, or a lower than expected frictionfactor.

A mounting means 105 is associated with the sliding actuator cam 35 andthe flange 506 for slidably mounting the sliding actuator cam 35 to thetubular carrier body 50 in a fixed rotational orientation. A biasingmeans 110 is associated with the mounting means 105 for biasing thesliding actuator cam 35 away from the flange 506.

In a preferred embodiment, the means 105 is formed by shafts 386 whichare slidably received by the flange 506 and fixedly mounted to the firstend 352 of the sliding actuator cam 35. The biasing means 110 comprisescoil springs 112 surrounding the shafts 386 and positioned between theflange 506 and the actuator cam 35 to urge the actuator cam 35 away fromthe flange 506. (See also FIG. 1).

As the carrier body is lowered, the wedge contacts the penetrator andmoves it toward the first position. When the penetrator seats in thefirst position, the carrier body is not yet bottomed against its stopand continues moving with respect to the wedge. The shafts 386 areslidably received and taken up in the boreholes 518 in the flange 506until the carrier body bottoms against its stop.

WEDGE-DETENT

With reference to FIG. 17, the sliding actuator cam 35 has a first end352, a second end 354, and a longitudinal axis extending between thefirst end and the second end. The actuator cam 35 has a first sidesurface 358 and a generally planar cam surface 360. The cam surface 360extends at an angle in the range of about 2 degrees to about 10 degreeswith respect to the longitudinal axis. A detent means 115 is associatedwith the first side surface 358 of the sliding actuator cam 35 forlimiting relative movement between the sliding actuator cam 35 and thedetent means 115 along the longitudinal axis of the sliding actuator cam35 when the detent means is engaged with the sliding actuator cam 35. Amounting means 120 is associated with the detent means 115 and thesliding actuator cam 35 for movably mounting the detent means 115 withrespect to the sliding actuator cam 35 when the detent means isdisengaged from the sliding actuator cam 35. In one embodiment of theinvention, the detent means comprises the pawl 45. In a preferredembodiment of the invention, the mounting means comprises the carrierbody 50 and the mounting means 105.

In another and preferred embodiment of the invention, and with referenceto FIG. 22, the sliding actuator cam 635 has a first end 652, a secondend 654, and a longitudinal axis extending between the first end and thesecond end. The actuator cam 635 has a first side surface 658 and agenerally planar cam surface 660. (See FIG. 20). The cam surface 660extends at an angle in the range of about 2 degrees to about 10 degreeswith respect to the longitudinal axis. A detent means 715 is associatedwith the first side surface 658 of the sliding actuator cam 635 forlimiting relative movement between the sliding actuator cam 635 and thedetent means 715 along the longitudinal axis of the sliding actuator cam635 when the detent means is engaged with the sliding actuator cam 635.A mounting means, not shown in FIG. 22 but which can be the same as themounting means 120, is associated with the detent means 715 and thesliding actuator cam 35 for movably mounting the detent means 715 withrespect to the sliding actuator cam 635 when the detent means isdisengaged from the sliding actuator cam 635. In one embodiment of theinvention, the detent means comprises the pawl 700. In a preferredembodiment of the invention, the mounting means comprises the carrierbody 50 and the mounting means 105.

As the carrier body is lowered, the wedge contacts the penetrator andmoves it toward the first position. When the penetrator seats in thefirst position, the carrier body is not yet bottomed against its stopand continues moving with respect to the wedge. This causes the detentto release and continue travel with the carrier body until the carrierbody seats against its stop. When the carrier body is raised, the detentreengages the wedge. The detent moves from a first position, a shown inFIG. 15, which is in engagement with wedge, to a second position, asshown in FIG. 18, which is spaced apart from the wedge. When the pawl 45is used as the detent, the surface 470 contacts the surface 374 when thepawl is in the first position. When the pawl 700 is used as the detent,the surfaces 720 and 722 contact the surfaces 684 and 690 when the pawlis in the first position. See FIG. 22.

CARRIER BODY-DETENT

With reference to FIG. 15, the carrier body 50 has a first end 502, asecond end 504, and a longitudinal axis extending between the first endand the second end. The carrier body 50 is generally tubular and has agenerally annular flange 506 positioned at the first end 502 and agenerally tubular nose-piece 510 protruding from a face of the flange506. The nose-piece 510 has a generally cylindrical exterior surface514. The pawl 45 is mounted to the tubular carrier body 50. The pawl 45is formed from an elongated member 452 having a first end 454 which isspaced apart from the tubular carrier body and a second end 456 which isfixedly attached to the tubular carrier body 50. The elongated member452 extends generally longitudinally along the generally cylindricalexterior surface 514 of the nose piece 510 and has a first generallyplanar face 464 with a tooth element 468 protruding from the firstgenerally planar face 464 at a position adjacent to the first end 454 ofthe elongated member 452. The elongated member 452 has second generallyplanar face 466 which faces the generally cylindrical exterior surface514 of the tubular carrier body 50. The detent 700 can be mounted to thecarrier body 50 in the same manner as the pawl 45. Preferably, when thedetent 45 is employed, the second elongated member 458 is received bythe channel 528 in the carrier body. When the detent 700 is employed,the connecting member 706 is received by the channel 528 in the carrierbody. In both cases, the pawl arms are positioned in a channel 516 inthe carrier body to minimize required radial clearance between thecarrier ring and the carrier body.

CARRIER BODY-RETRACTOR

With reference to FIG. 18, the carrier body 50 has a first end 502, asecond end 504, and a longitudinal axis extending between the first endand the second end. The carrier body 50 is generally tubular and has agenerally annular flange 506 positioned at the first end 502 and agenerally tubular nose-piece 510 protruding from a face of the flange506. The nose-piece 510 has a generally cylindrical exterior surface514. The retractor cam 40 comprises a base plate 402 and at least oneretractor arm 406 mounted to the base plate. The base plate 402 ismounted to the generally cylindrical exterior surface 514 of the tubularcarrier body 50 and the at least one retractor arm 406 protrudes fromthe base plate 402. Preferably, a pair of retractor arms 406 are mountedto the base plate. The pair of retractor arms are equidistant from theflange 506. Each retractor arm has an inner end 408 attached to the baseplate 402 and an outer end 410. A side edge of each arm forms a cammingsurface 412 which faces generally longitudinally along the tubularcarrier body 50. Each of the pair of parallel retractor arms 406 tapersfrom the outer end 410 to the inner end 408 so that the camming surfaces412 one in a plane which forms an angle in the range of about 20 degreesto about 60 degrees with respect to the longitudinal axis of the tubularcarrier body 50.

Preferably, the base plate 404 of the retractor 40 is mounted in thechannel 526 of the carrier body. The channel 526 is positioned betweenthe channel 528 and the flange 506 of the carrier body.

COMBINATION

A tubular member 550 preferably in the form of a spool body 55 has agenerally cylindrical inside surface 552 and an outside surface 554 anda longitudinal axis. The carrier ring 30 has a generally cylindricalinside surface 308 and a generally cylindrical outside surface 310 and alongitudinal axis. The carrier ring 30 is positioned coaxially in thetubular member 550 with the outside surface of the carrier ringpositioned adjacent to the inside surface of the tubular member 550. Thecoupling element 20 is carried by the carrier ring 30. The couplingelement 20 has a longitudinal axis which is generally radiallypositioned with respect to the longitudinal axis of the carrier ring 30.The coupling element has an inner end and an outer end, the outer endhaving a sealing face. A means 251 defines a sealing face on the insidesurface of the tubular member 550. The sealing face of the firstcoupling element sealing engages the sealing face defined by the meanson the inside surface of the tubular member 550. A means 120 is providedfor urging the sealing face of the coupling element and the sealing facedefined by the means on the tubular member 550 together responsive torelative longitudinal movement between the means for urging and thetubular member 550.

In a preferred embodiment, the means 120 comprises the carrier body 50,the sliding actuator cam 635 and the pawl 700. The means 251 comprisesthe coupling element 25.

MODULAR UNIT

One of the features of the present invention is that penetrator movementis cammed by the relative movement between two cylinders. If the movablepenetrator is on the inner cylinder, it can be constructed as part of afree standing modular assembly. This would allow attachment to a widevariety of tubing hanger designs.

The whole arrangement can be beneficially arranged so that the largerpart of the vertical extent of the system hangs down into the well,rather than adding to the stack-up height of (especially) the tubingspool.

The modular unit comprises a carrier ring 30. The carrier ring 30 has agenerally cylindrical inside surface 308 and a generally cylindricaloutside surface 310. A coupling element 20 is carried by the carrierring. The coupling element has a longitudinal axis which is generallyradially positioned with respect to the longitudinal axis of the carrierring. The coupling element has an inner end and an outer end and theouter end has a sealing face. A carrier body 50 having a generallycylindrical outside surface is positioned coaxially inside of thecarrier ring 30. The generally cylindrical outside surface of thecarrier body is adjacent to the generally cylindrical inside surface ofthe carrier ring. A means 121 is provided for radially moving thecoupling element in the carrier ring responsive to relative longitudinalmovement between the carrier ring and the carrier body.

The means 212 for radially moving the coupling element preferablyincludes a sliding actuator cam 35 positioned adjacent to the inner endof the coupling element 20 and a mounting means 105 associated with thesliding actuator cam and the carrier body for slidably mounting thesliding actuator cam 35 to the carrier body 50. Preferably, there isprovided a mounting means 95 for slidably mounting the carrier ring tothe carrier body in a fixed rotational orientation.

METHOD TO USE

According to certain aspects of the invention, there is provided amethod for establishing a line connection across a first tubular membersidewall. A carrier ring is provided which is concentrically positionedin the first tubular member. An annulus is defined between the carrierring and the first tubular member. A line coupling element is carried bythe carrier ring. The line coupling element has a longitudinal axiswhich is generally radially directed with respect to a longitudinal axisof the carrier ring. The line coupling element has an outer end whichdefines a first sealing face. A mean is provided for defining agenerally radially extending passage through the sidewall of the firsttubular member with a second sealing face being defined at an inner endof the passage. The second sealing face is for sealingly contacting arespective first sealing face of the coupling element. A means isprovided for urging the sealing face of the first coupling element andthe sealing face at the inner end of the passage together in response torelative longitudinal movement between the first tubular member and themeans for urging.

The method is especially well suited for establishing a radial lineconnection across a spool body. A carrier ring assembly formed by acarrier ring with a carrier body is concentrically mounted in the spoolbody. An annulus is defined between the carrier ring and the spool body.At least one first coupling means is carried by the carrier ring. Eachcoupling means has an outer end forming a first sealing face. A likenumber of second coupling elements are provided in the form of radialpassages in the spool body. The inner ends of the passages form secondsealing faces. A means is provided for radially urging the firstcoupling means towards the radial passages in response to relativelongitudinal movement between the spool body and the carrier body. Thereactive longitudinal movement between the carrier body and the spoolbody causes a sealing engagement between said first and second sealingfaces. In a further embodiment, the method comprises providing means forwithdrawing said first coupling means from sealing engagement with saidradial passages. In a still further embodiment, the method comprisesproviding means to align the first and second sealing faces.

What is claimed is:
 1. A coupling element having a first end, a secondend, an outer surface, and a longitudinal axis extending between thefirst end and the second end, the first end of the coupling elementdefines a sealing surface which extends normally to the longitudinalaxis, and the outer surface defines a cam follower surface forming anangle in the range of from about 2 to about 10 degrees with respect tothe longitudinal axis;wherein the second end defines the cam followersurface and the coupling element defines a passage extending from thesealing surface to the outer surface.
 2. A coupling element as in claim1 wherein the outer surface further defines at least one second camfollower surface forming an angle in the range of about 10 degrees toabout 45 degrees with respect to the longitudinal axis.
 3. A couplingelement as in claim 2 wherein the outer surface is cylindrically shapedwith a circumferentially extending groove and the second cam followersurface is formed by a wall of the groove.
 4. A coupling element as inclaim 1 wherein the coupling element has a valve seat positioned in thepassage adjacent to the sealing surface, said valve seat facing awayfrom the sealing surface, said coupling element further comprisingavalve element positioned in a generally longitudinally extending portionof the passage adjacent to the sealing surface, said valve elementhaving a valve face to sealingly contact the valve seat; and means forbiasing the valve element toward the valve seat.
 5. A coupling elementas in claim 4 wherein the valve element has a first end and a second endand the valve face is positioned between the first end and the secondend, the second end of the valve element protruding from the first endof the coupling element when the valve face of the valve element is insealing contact with the valve seat.
 6. A coupling element as in claim 1further comprising a plug positioned at the second end.
 7. A couplingelement as in claim 6 wherein the passage opens onto a side surface ofthe coupling element, said element further comprising a tubing connectedto said passage at said side surface.
 8. A coupling element as in claim6 wherein the sealing surface is planar.
 9. A coupling element as inclaim 1 further defining a plurality of grooves on the sealing surfaceconcentrically spaced around an inlet end of the passage.
 10. A couplingelement as in claim 9 further comprising a plurality of seal elementspositioned in the plurality of concentrically spaced grooves, one sealelement per groove.
 11. Apparatus comprisinga tubular member having agenerally cylindrical inside surface and an outside surface and alongitudinal axis; a carrier ring having a generally cylindrical insidesurface and a generally cylindrical outside surface and a longitudinalaxis positioned coaxially in the tubular member with the outside surfaceof the carrier ring positioned adjacent to the inside surface of thetubular member; a first coupling element carried in the carrier ringhaving a first end and a second end and defining a passage extendingaway from the second end, said first coupling element defining a valveseat positioned in the passage adjacent to the second end and facingaway from the second end; a second coupling element having a first endand a second end, said second coupling element defining a passageextending away from the second end and further defining a landingsurface for a valve body at the second end; a valve element positionedin the passage near the first end of the first coupling element, saidvalve element having a first end and a second end and a valve facepositioned between the first end and the second end which faces thefirst end of the first coupling element, the second end of the valvebody being in contact with the valve body land on the second couplingelement to hold the valve face off of the valve seat; means associatedwith the first coupling element for biasing the valve body toward thevalve body land and the first coupling element away from the secondcoupling element, and means associated with the first coupling elementand the second coupling element for urging the first coupling elementinto contact with the second coupling element; wherein the means forurging includes a carrier body having a generally cylindrical outsidesurface positioned coaxially inside of the carrier ring with thegenerally cylindrical outside surface of the carrier body positionedadjacent to the generally cylindrical inside surface of the carrierring.
 12. Apparatus comprisinga coupling element having an exteriorsurface, a first end, a second end, and a longitudinal axis extendingbetween the first end and the second end, said coupling element defininga passage having a first diameter extending from the first end along thelongitudinal axis, wherein the exterior surface at said second end ofthe coupling element defines a cam follower surface, said couplingelement having a valve seat facing the second end positioned in thepassage adjacent to the first end, a valve element positioned in thepassage adjacent to the sealing surface, said valve element having avalve face to sealingly contact the valve seat and a nipple having asecond diameter which is smaller than the first diameter extending pastthe valve face to protrude from the first end of the coupling elementwhen the valve face is positioned against the valve seat; and meansassociated with the valve element and the coupling element for biasingthe valve face toward the valve seat.